Mining machine



Aug. 29, 1939. L. E. MITCHELL MINING MACHINE Original Filed April 25 1956 7 Sheets-Sheet 1 f/VVE/VTOR: LEwss E. MITCHELL, BY

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ATT'X 1939. E. MIYI'CHELL I 2,171,161

MINING MACHINE Original Filed April 25, 1936 7 Sheets-Sheet 2 f/vvE/v oR: LEWIS E. MITCH E ATT'X IZI Aug. 29,' 1939.

L E MITCHELL 2,171,161

MINING MACHINE Original Filed April 25, 1936 7 Sheets-Sheet 3 //v VE/Y TOR.

LEWIS E. MITCHELIU ATT'X Aug. 29, 1939. L. E. MITCHELL 2,171,161

MINING MACHINE Originai Filed April 25 1936 7 Sheets-Sheet 4 L. E MITCHELL 2,171,161

MINING MACHINE 7 Sheets-Sheet 5 Aug. 29, 1939.

' Original Filed April 25, 1936.

fM/E/y TOR: LEWIS E MITCHELL, BY

Aug. 29, 1939'. L. MITCHELL 2,171,161

MINING MACHINE Original Filed April 25, 1936 7 Sheets-Sheet 6 I40 I38 c',

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//VVEN7O/?.' L EWlS MITCHELL) BY L E MITCHELL MINING MACHINE Aug. 29, 1939.

Original Filed April 25, 1936 '7 Sheets-Sheet 7 [/y VE/VTOR.

LEWIS E MITCHELL,

ATT'Y.

Patented Aug. 29, 1939 UNiTED STATES PATENT OFFIQE MINING MACHINE Lewis E. Mitchell, Columbus, Ohio, assignor to The Jeffrey Manufacturing Company, a corporation of Ohio 11 Claims. (01. 262-48) This invention relates to a mining machine and more particularly to a mining machine adapted to cut horizontal kerfs at varying elevations in a coal mine.

An object of the invention is to provide a mining machine of the above mentioned type having a frame with a fiat bottom adapted to rest directly on a mine floor and to slide thereover, which machine is provided with a horizontal kerf cutter unit which may be adjusted in elevation and provided with draft means pulling directly on said unit, thereby to cut horizontal kerfs at various heights.

Another object of the invention is to provide a very compact but highly flexible mining machine.

Another object of the invention is the provision of an improved apron guard connected to a cutter bar and movable up and down therewith while overlapping the front end of the frame of a mining machine.

A further object of the invention is the provision of improved connections on a mining machine for the free end of a feeding rope con.- nected to mechanism for sliding the mining machine over the mine bottom while the top kerfcutter thereof is adjusted to various elevations.

Other objects of the invention will appear hereinafter, the novel features and combinations being set forth in the appended claims.

This application is a division of my application Serial No. 76A56, filed April 25, 1936, for an improvement in a Mining machine.

In the accompanying drawings,

Fig. l is an plan view of the mining machine comprising my invention with the cutter bar out off to reduce the length of the drawing;

Fig. 2 is a side elevational View of the device of Fig. 1;

' Fig. 3 is an elevational sectional view taken on the line 3-3 of Fig. 1 looking in the direction of the arrows;

Fig. 4 is a sectional plan view taken on the line 44 of Fig. 3 looking in the direction of the arrows;

Fig. 5 is a sectional elevational view taken on the line 5--5 of Fig. 1 looking in the direction of the arrows;

Fig. 6 is a sectional elevational view taken on the line 5-5 of Fig. 4 looking in the direction of the arrows;

Fig. '7 is a sectional plan view of a portion of the machine taken on the line of Fig. 6 looking in the direction of the arrows;

Fig. 8- is a sectional. elevational view taken on the line 3-8 of Fig. 1 looking in the direction of the arrows;

Fig. 9 is a plan and sectional view of a detail taken on the line 99 of Fig. 3 looking in the direction of the arrows;

Fig. 10 is a sectional plan view of the planetary gear mechanism taken on the line lllli of Fig. 3 looking in the direction of the arrows;

Fig. 11 is a plan and sectional view taken on the line H!l of Fig. 3 looking in the direction of the arrows;

Fig. 12 is a sectional View of a detail taken on the line I2|2 of Fig. 4 looking in the direction of the arrows; and

Fig. 13 is an end elevational view taken on the line |3-l3 of Fig. 12 looking in the direction of the arrows.

The mining machine herein disclosed is generally of the Shortwall type, that is, it is generally employed in a relatively wide room for cutting horizontal kerfs across the face of the mine room. It is particularly constructed for a room and pillar type of mining system employing conveyors in which there will be a face conveyor Which runs parallel to the room face and feeds a room conveyor which runs parallel to a rib of the room, said room conveyor feeding entry conveyors of the complete system which will load mine cars.

It is desirable to keep the length of the main frame of the mining machine as short as possible to the end that the face conveyor may be maintained asclose to the mine face as possible, whereby supporting timbers or roof props may be provided relatively close to the mine face. It is, of course, evident that both the face conveyor and the mining machine must work between the roof propping timbers and the mine face.

Referring particularly to Figs. 1 and 2 of the drawings it is to be seen that the mining machine comprises a main frame to which is attached for vertical adjustment a kerf cutting mechanism H. The main frame Zii is formed of two sections comprising the motor section 22 and the gearing section 23, which sections 22 and 23 are removably attached together as by nuts and bolts 24. By removing the nuts 24, 24, the motor section 22 may be entirely removed from the main frame 20.

The section 23 is welded to and carried upon a fiat bottom or skid pan 25 (Figs. 2 and 6) which is adapted to rest upon and slide over the floor of a mine room. The motor section 22 the bot' tom of which is flush with the bottom of the pan 25 in direct contact with the mine bottom,

comprises a housing within which is mounted an electric motor 25 provided with a rotating armature shaft 2? (Fig. 3) extending into the housing of the gearing section 23 on a horizontal longitudinal axis. To provide access to the brushes of the motor 26, the housing of the motor section 22 is also provided with a pair of flame-proof removable caps 28, 28. (Fig. 1.)

Rigidly attached to and forming a part of the motor section 22 is a control box 29 for the electric motor 26, which is provided with a removable fiame-proof cap 34 (Fig. 2) to provide access to the controls therein. A control lever 32 and a reverse lever 34 are provided for controlling appropriate switches within the switch-box 29, for starting the motor 25 and for reversing its direction of rotation. (Fig. l.)

Adjacent the rear central portion of the motor section 22, is provided a detachable guide sheave 33, Fig. 1, the details of which are illustrated in Fig. and will be described more in detail hereinafter.

Also associated with the trailing side of the motor section 22, at that corner thereof remote from the working face of the mine vein, are mounted on the bottom plate 22, Figs. 1, 2 and 5, the guide rollers or pulleys 336 and 33'! whichmay be alternately engaged by a retarding or guide rope or cable 34. The leading side of the motor section 22 as shown in Fig. 1 carries the cable guide rollers 38 and 39, the guide roller 38 being pivoted to a bracket fixed to the control box 29, while the guide roller 39 as shown in Fig. 2 is pivoted to brackets 40, 40 which in turn are pivotally connected as shown at 4!, 4|, Fig. 2, to brackets 4|, 4| secured to the motor control box 23. The guide roller 39 may be swung either to its full line position shown in Fig. 1 or to the dotted line position. The electric cable 42 shown in Fig. 1 leads from a distant source of electric power supply to the control box 29, and motor starting resistance 43 may be located in the frame of the motor section 22 in the position illustrated in Fig. 1.

By referring to Fig. 5 it will be seen that the retarding rope drum mechanism 35 comprises a drum 44 journaled on the stationary stub bearing 45 secured rigidly to the vertical plate 46 of the motor section 22. Secured to the vertical plate 46 is a frusto-conical clutch element 4! in position to co-operate with the brake lining 48 carried by the clutch element or brake drum 49 which is rigidly attached to the inner flange of the drum 44. By shifting the drum 44 longitudinally along the stub bearing 45, the retarding force affected by the cone clutch or brake may be effectually adjusted.

In order to shift the drum 44 to partially apply the slip clutch shown in Fig. 5, I provide a threaded rod 50 adapted to be received by the threaded bore 5| in the axial center of the stub bearing 45, and key a hand wheel 52 to the outer end of the rod 53. The wheel 52 has a hub 53 the inner side of which engages the anti-friction bearing 54 mounted within the cup 54' at the center of the outer flange of the rope drum 44. A collar 55 on the rod 50 is located within the drum 44 as shown in Fig. 5, in position to assure movement of the drum 44 axially of the bearing 45 when the wheel 52 is rotated. The rod 50 is freely rotatable relatively to the rope drum 44 but rotation of the rod 53 by means of the wheel 52 will rotate the inner threaded end in the threaded bore 5! and thereby cause movement of the clutch elements 41, 49 toward or away from each other.

The kerf-cutting mechanism 2! shown in Figs. 1, 2 and 3, comprises a flat horizontal cutter bar 55 mounted upon and rigidly attached to a cutter bar support or head 51. The kerf-cutting mechanism is adjustable along vertical lines with respect to the main frame 23 and the operating mechanism enclosed thereby.

'An endless cutter chain 58 is provided with reversible cutter bits 59 and is adapted to travel around the cutter bar when driven by the sprocket 60 which is mounted upon and keyed to a clutch element 6! as shown in Fig. 3. The sprocket 50 and clutch element 6| are mounted upon a bracket 63 with the ball bearing element 64 intervening. The bracket 63 is shown in Fig. 3, removably attached to the cutter bar support frame or head 51 by means of machine screws 65. The clutch element BI is mounted upon a journal bearing 66 carried upon a stub shaft 67 which is provided with a cap 68 overlying the clutch element and the hub of the sprocket 60.

The stub shaft 67 is secured by means of the transverse rivet to the upper end of the hollow or tubular shaft 69 which is splined both internally and externally. By means of the clutch mechanism 7!, shown in detail in Figs. 3 and 9, the motor 26 may be connected through the vertical tubular shaft 69 to the sprocket 50 to drive the same, as will be hereinafter more fully explained.

As shown in Figs. 2, 3 and 9, the vertical tubular drive shaft 69 is provided with external splines 12 which are engaged by the clutch element 13. The upper side of the clutch element 13 is provided with jaws 14 adapted to co-operate with the jaws B2 on the underside of the clutch element 5|. By means of manually operated mechanism the clutch element 73 can be slid vertically with respect to the splined tubular drive shaft 69, to effect a driving connection between the vertical tubular drive shaft 59 and the clutch element 6| to effect rotation of the driving sprocket 60 of the chain kerf cutter.

Manually operated mechanism for applying or releasing the clutch 7! is shown particularly in Figs. 3 and 9. A shipper comprising a yoke has a semi-circular groove which fits a circular flange 16 integral with the clutch element 13. It will be evident that free rotary movement is permitted between the flange l6 and the yoke 15. When the chain cutter is being driven, the vertical tubular shaft 69 is being rotated, and since the clutch element i3 is splined to the exterior of the tubular shaft 69, this clutch element will also be rotated and consequently the circular flange It will be rotated in the semi-circular groove of the yoke 75 when the chain cutter is being driven by rotation of the sprocket 60. l

The yoke 15 is provided with trunnions H, H (Fig. 9) journaled in bearings at the outer ends of the lever arms l8, 48 which are pivoted to the transverse shaft 79 which is carried by a pair of bosses 3B, 83 screw-threadedly attached to a bottom plate 8! (Fig. 3) of the cutter bar support or head 57.

It should be understood that the operating mechanism for the clutch H must be secured to the cutter bar support frame or head so as to move up and down bodily therewith as the kerfcutting unit is adjusted in elevation relative to the main frame 23, as shown in Fig. 2.

A pair of brackets 82, 82 welded to each other, as shown in Fig. 9, are pivotally mounted on the supporting shaft 19, and are connected to stub shafts 83, 83 by means of the transverse pins 84, 84. The rear ends of the arms l8, 18 are pivoted to the stub shafts 83, B3. Removable cotter pins 85, 85 are provided on the ends of the shaft 19 to maintain the arms 18, 18 in proper relation to the other parts shown in Fig. 9. By removing the cotter pins 85, 85, the arms 18, 18 may be removed to disassemble the entire shipper mechanism for renewal or repairs.

Extending between the U-shaped arms of the brackets 82, 82 and pivotally mounted with respect thereto is a trunnion 86 which is provided with a central transverse aperture adapted to receive an eccentric extension 8? eccentrically mounted upon a cylinder 88 which is rotatably journaled in the bearing 89 carried by the bottom plate 8i, as shown in Fig. 3. A cotter pin 90 is provided to maintain the extension 8'! in the trunnion 86 and to permit removal thereof. The journal bearing 89 is provided with a pair of laterally extending abutments or stops 9|, Bl which are adapted to limit the throw of a handle 92 which is pivotally attached to the cylinder 88 by means of a pin 93.

The handle 92 is provided with a cam 94 adapted to co-operate with a spring-pressed plunger 95 which tends to retain the handle 92 either in the full line position in Fig. 9 or in the dotted line position. When the handle 92 is in its full line position, as illustrated in Fig. 9, it occupies the position shown in Fig. 3. The eccentric extension Bl will then be in its uppermost position. This will rock the arms 18 about the pivot shaft F9 to move the yoke 15 to its lower position to release the clutch H. The handle 92 has a movement through a semi-circular path and the limit stops 9| may be in the nature of clips comprising spaced-apart plates of different lengths with a groove in between for entrance of the lever 52. The pivot 93 may be an eccentric and the spring-pressed plunger 95 may act to hold the arm 92 in. either the clip ill where the clutch i! will be applied, or in the other clip 9i where the clutch will be released. It will thus be seen that the clips iii, 9! may be used to positively hold the clutch ll of Fig. 3 either in its applied position or in. its released position.

In order to apply or release the clutch H of Fig. 3, the handle 92 of Fig. 9 is first swung about the eccentric pivot 93 which assists in moving the lever Q2 away from the clip 9i. When the lever 92 is moved from its full line position to its dotted line position as shown in Fig. 9, the eccentric extension 8'! of l igv 3 will be moved to its lowermost position, thus lifting the yoke '15 and thereby causing engagement between the jaws 62 and it of the clutch elements 6! and 13 of the clutch it. This clutch mechanism H therefore provides means for eifecting a driving connection between the vertical tubular shaft 69 and the cutter chain 58, but it should be particularly noted that by locating the clutch H between the upper end of the tubular shaft 69 and the sprocket 69, the motor 25 may be operated to rotate the haulage rope drum while the cutter chain is not being driven.

As shown in Figs. 2 and 3, the cutter bar support or head 51 carries a depending apron having the shape shown in Figs. 2 and 4 and serving as a shield or guard plate for the elevating mechanism hereinafter described, and also as a vertical guard plate overlapping the front end of the main frame, as shown in Fig. 2, in position to abut against the Working face of the mine vein when the kerf cutter is being fed transversely of itself along such mine vein. The apron which is secured to the cutter bar support or head 51 and depends therefrom, as shown in Figs. 2 and 3, comprises a front downwardly extending plate 96 and a pair of downwardly extending side plates 97, 9? which are rigidly secured by Welding to the bottom plate 8!. The

front plate 96 preferably tapers toward the rear at each side and is provided with a connecting crosspiece 9'! at its rear end, as shown in Figs. 1; 2 and 3.

The front plate 96 is provided with hooks 98, 98, Fig. 1, on opposite sides of the cutter bar and spaced below the same, as shown in Fig. 2. Also rigidly attached to the bottom plate M as well as to the front and side plates 96 and 91', on opposite sides of the cutter bar, are attaching brackets 99, 99 each provided with a pin lilil adapted to be attached to a coupling member 561 of the feed cable 532. As will be more fully described hereinafter, the cable 102 extends from either side of the mining machine toa pulley secured to an anchorage in the mine distant from the mining machine. The feed rope I82 is reeved around such pulley and its free end brought back for connection either to one of the anchorage hooks 8B or to one of the anchorage pins I08. When the kerf cutter is in its lowermost position and the coal being cut is relatively soft, the free end of the feed rope I92 may be connected to either of the anchorages 98. But when the kerf cutter occupies its topmost position or when the coal being cut is relatively hard, it becomes necessary to connect the free end of the feed rope closer to the cutter bar or to either of the attaching brackets 95 The feeding resistance met with by the chain kerf cutter must be balanced against the frictional resistance between the supporting pan 25 and the mine bottom, by so arranging the feed rope Hit? in connection with the distant anchorage, and the free end of the rope in proper relation to the mining machine as a whole, with the kerf cutter at adjusted elevation.

As shown in Figs. 2, 3 and 8, the housing for the gearing of section 23 of the mining machine comprises a removable top part attached to a lower part. The lower part is composed of end walls H33, H94 and side walls H95, I85. I93, IM and 505 are all rigidly attached to the bottom or skid pan 25, as by welding. The top part of the gearing housing comprises a bot om plate M31, as shown in Fig. 8, welded to end plates I08, [69, as shown in Fig. 3, and also welded to side plates HG, Hi as shown in Fig. 6. The top part of the gearing section 23 of the mining machine is removably attached to the lower part by means of the bolts use, We, as shown in Figs. 2 and 6. The bottom of the lower part of the housing is closed by the skid pan plate 25. In fact, the lower part comprising the bottom plate 25, the end walls 993, IM and the side Walls H25. H95, constitutes the skid pan, removably secured by means of the bolts I96 to the upper part of the gear housing 23. The upper part of the housing of the gear section 23 is removably secured to the motor section 22 by means of the bolts 2 3, 24, as shown in Figs. 1 and 4.

The upper part of the housing of the gear section 23 is also provided with a horizontal reinforcing plate I l s rigidly secured to the side plates H6 and to the end plate 9%. The horizontal plate H8 intermediate the bottom plate It? and the top plate ill, shown in Fig, 3, is Welded to The walls the vertical tube I20 which extends downwardly and is welded at its lower end to the bottom plate It]? to provide ample space for the elevating mechanism connected between the bottom part of the gear housing and the cutter bar, as shown in Fig. 3. The plate H8 is also welded to the vertical guide cylinders IE9 which form parts of the telescopic guiding mechanism spaced from the elevating device and located between the cutter head 5? and the gear section 23, as shown in Figs. 1 and 8. The plate H8 is provided with a large circular opening for the feeding rope drum Hi l, as shown in Fig. 3; but, nevertheless, the plate 5 It! extends over a Wide area, as shown in Figs. 4 and '7, to provide support for the mechanism by means of which the feeding rope drum is controlled.

As shown in Fig. 8, the cutter head 5'! is provided with laterally extending reinforcing plates Ifi which are rigidly secured to the plate 85, which is the bottom plate of the kerf cutting unit, as shown in Figs. 1, 2 and 3.

The kerf cutting elevating mechanism will now be described. Centrally disposed with respect to the cutter head 5? and along a vertical axis which is substantially through the center of gravity of the adjustable kerf cutting unit 2|, I provide a vertical threaded shaft I22 having an upper neck 523 which is rigidly attached to the cut ter bar 55 and the cutter head 51. The vertical shaft I 22 is screw-threaded through the upper end of the vertical tubular shaft F24 mounted for rotation in the cup bearing I25 carried by the bottom plate 25. The upper end of the tubular nut shaft 524 is journalecl in the cup bearing I26 which may be welded to the top plate I I I shown in Fig. 3.

The upper cup bearing I26 is provided with a lubrication moat I21 having a lubricating opening I28, as shown in Fig. 3. Lubricating material is supplied to the moat I2! by a downwardly extending tube I29 carried by the cutter head 5'! and co-operating with the grease fitting I30. Lubricating material supplied by the moat I2I will lubricate not only the cup bearing I25 but also the upper nut portion I35 of the tubular shaft 12d, and lubricant may also be expected to seep through the nut I3! and along the screwtlireaded shaft I22 and through the bottom thereof to the cup bearing I25.

The lower end I32 of the tubular shaft I24 is journaled in the cup bearing I25 and provided at its lower end with an annular shoulder to receive the disk plate Iit'! through an opening in the center of which extends upwardly the hardened bearing pin I33. The lower end of the pin 533 is provided with a circular head, the underside of which may have the shape of a segment of sphere so as to make point contact with hardened. bearing plate I35 resting in a recess in the bottom of the cup 525, as shown in 3. As before stated, lubricant introduced into the moat 121 can by seepage find its way into the cup I25 to lubricate the pin bearing as well as the cup bearing I25.

F yed to the lower end portion of the tubular r 52 1 is a sprocket I35 connected by the endless sprocket chain I3! to a sprocket 56 to be driven thereby when the clutch M9 is applied. When the sprocket its is rotated, the nut I 3! at the upper end of the tubular shaft I2 5 will be rotated. and since the threaded shaft 122 is held against rotation by its rigid attachment to the cutter bar 56 and cutter head 51, rotation of the nut I3! will result in variation in elevation of the kerf cutting unit. The nut I8I is rotatable in reverse directions and therefore the kerf cutting unit may be elevated or lowered, as desired.

On opposite sides of the cutter head I provide telescopic guiding mechanism which serves not only to guide the kerf cutting unit along vertical lines when adjusted in elevation, but also to co-operate with the spaced-apart vertical hollow shafts 69, I24 and the mechanism connecting the same to the kerf cutting unit, to distribute the feeding strains as the machine is fed by means of the rope feeding mechanism over the mine bottom, particularly when the kerf cutting unit is at relatively high elevation.

The two telescopic guiding mechanisms are substantially the same construction and therefore common reference characters are used for similar elements. Each of said guiding mechanisms comprises a heavy depending shaft or cylinder 5% which is removably secured by means of a pin to the attaching bracket 99, as shown In Fig. 8. A vertical cylindrical opening through the bracket 139 receives the upper end of the cylinder I38, and the transverse pin 548 extends through the bracket and transversely through the cylinder E39, and the ends of the pin I40 receive cotter pins MI (Fig. l) to retain the cylinder I38 in position to always move bodily with the kerf cutting unit. The parts of the telescopic guiding mechanisms are close fitting as they are designed to resist all the feeding strains.

Surrounding each shaft I38 is a pair of concentric cylinders I42 and I 43 each movable upwardly and downwardly relatively to the main frame. The cylinder M3 fits in the cylinder HP] to slide vertically therein, and the cylinder 42 fits in the cylinder M3 to slide vertically therein after the latter has reached the limit of its upward movement. Adjacent the bottoms of the cylinders M2, I43 and H9 cylindrical recesses provide annular shoulders for engagement by the circular collars or flanges Hi l, I65 and 54% one after another. It will thus be seen that telescopic guiding devices are provided on opposite sides or" the main frame and between the latter and opposite sides of the kerf cutting unit. These guiding devices are entirely separate from the screw-threaded lifting device and also entirely separate from the tubular shaft $9. These tubular guiding devices are located at the extreme front corners of the main frame and on opposite sides of the kerf cutting unit so that irrespective of the direction of feeding movement transversely of the kerf cutter, the guiding devices will be in position to resist the feeding strains. During kerf cutting operations the neck 523i fits loosely in the parts to which connected as shown in Fig. 8, and likewise the screw l22 fits loosely in the nut I3I; consequently the telescopic guiding devices will resist all the feeding strains during feedingmovements. While the guiding devices are entirely separate and independent of the lifting mechanism, as shown in Fig. 4, such guiding devices are in the most eflicient position to prevent feeding strains from being imparted to either the lifting screw mechanism or the tubular drive shaft 69, and consequently while the cutter bar is rigidly connected to the main frame by means of the two telescopic guiding devices, the vertical tubular drive shaft 69 may be most efficiently rotated without tendency toward binding even when the kerf cutting unit is in its most elevated position. Likewise, the lifting mechanism does not tend to bind and may be operated at intervals by increments during feed.

.the cylinder I 42.

The limit of the upward sliding movement will be reached when the circular flange I56 of the cylinder I43 engages the annular shoulder of the cylinder N9, the latter being fixed to the main frame.

The machanism for controlling the rotation of the vertical tubular shaft I24 cf the kerf cuttin elevating mechanism, is shown in Figs. 3 and 11. Extenchng upwardly into the splined tubular drive shaft 69 is a vertical shaft I41, the upper end of which is feathered to the internal splines of the tubular drive shaft 69 to permit relative longitudinal movement therebetween but to transfer the rotary movement of the tubular drive shaft 69 to the shaft I41 through the keys I43. Between the shaft I41 and the drive chain I31 I provide a friction clutch I49 comprising a clutch disk I59 having a hub I 55' keyed to the lower end of the shaft I41. The lower end of the shaft I4? is provided with a hardened bearing :pin I53 co-operating with a hardened bearing plate I54 set into a recess at the center of a lubricating cup I54 on top of the bottom plate 25.

A shiftable clutch element 535 is provided with a shipper in the form of a split ring IE8 having trunnions I51, I51 which are journaled in the arms I53, I53 pivoted to a shaft I59 mounted upon bosses I69, I69 carried by the bottom plate 25, as shown in Fig. 11. The arms I68, I58 are rigidly attached to a bifurcated split bracket I6 I.

: A trunnion nut I62 co-operated with the bracket IGI and with the vertical threaded shaft I63, as shown in Figs. 6 and 11. By rotating the shaft I the arms I58, I58 will be rotated about the axis of the shaft I59 to control the application or release of the clutch I49.

Rigidly attached to the hub of the clutch element I55 is the sprocket I64 which receives the drive chain I31. The sprocket I64 is journaled on the bearing I65 carried by the lower tubular extension I66 rigidly attached to the bottom plate III! of the top portion of the housing or gearing section 23, as shown in Fig. 3.

By referring to Fig. 6, it will be seen that the vertical threaded shaft I63 is mounted between the bottom plate 25 and the removabletop plate III in position to be rotated by the hand wheel I66 which is keyed to the upper end of the shaft I63 and located outside of the main frame. Hardened bearing pin and plate means I61 is provided for the lower end of the shaft I63.

As shown in Fig. 1, the hand Wheel I66 is located in close proximity to the motor control box 29. While the clutch controlled drivin mechanism for the kerf cutter elevating appa- 1 :ratus is entirely enclosed within the main frame,

the clutch I49 may be operated from without the main frame by rotating the wheel I66 in one direction .or the other. The clutch I49 may thus be applied or released but the direction of elevation of the kerf cutting unit will depend upon the direction of rotation of the electric motor 26 which may easily be reversed at the motor control box 29.

The mechanism for driving the splined tubular tishaftr 69from the armature shaft 21 is shown in Fig. 3. The armature shaft 21 extends through an opening I 68 in the rear end wall I99 of the ear section 23. The shaft 21 carries a beveled pinion I 69 which is keyed to the shaft 21 and is removably held in place by a nut I19 on a screwthreaded extension I1I at the inner end of the shaft 21.

In mesh with beveled pinion I69 and mounted for free rotation on the axis of the vertical splined tubular drive shaft 69, is a large dish-shapedv bevel gear I12 provided with a hub portion I13 and a disk portion I13. Secured to the hub portion I13, preferably by welding, is a sleeve or cylinder I14 splined to the outer side of the vertical tubular drive shaft 69.

The hub portion I13 of the dish-shaped bevel gear I12is journaled to the bearing I15 carried by a downwardly extending cylindrical support I16 formed integral with the removable top plate I I I, as shown in Fig. 3. The splined sleeve portion I14 at the center of the dish-shaped bevel gear I12 is splined to the vertical drive shaft 69 so as to impart rotation thereto when the motor shaft 21 is rotated. The splined connection between the bevel gear I12 and the vertical tubular drive shaft 69 permits the latter to have free vertical axial movement when the kerf cutting unit is adjusted in elevation. That is to say, provision is made for driving the cutter chain 58 from the motor shaft 21 regardless of the elevated position of adjustment of the kerf cutting unit 2|.

A removable grease seal I11 may be provided at the top of the splined sleeve portion I14 to co-operate with the tubular drive shaft 69. Such grease seal is located on the gear section 23 at the place where the tubular shaft 69 emerges, as shown in Fig. 2.

It will thus be seen that motor operated mechanism is connected through the vertical tubular drive shaft 69 not only to the elevating mechanism butalso to the kerf cutting unit. The chain cutter should always be driven in the same direction with any given setting of the cutter bits 59, but when the clutch H is released and the clutch I49 applied, the electric motor 26 may safely be operated in reverse directions in accordance with the direction of elevation of the kerf cutting unit desired.

In order to assure proper intermeshing of the bevel gear I12 with the pinion I69, I provide a pair of hold-down rollers I18, I18 as shown in Fig. 4. These rollers I18 engage the upper beveled surface of the gear I12 where its circumference is at the maximum. As shown in Figs. 12 and- 13, each of the rollers I18 is supported by astub shaft I19 carried by downwardly extending brackets I80 rigidly secured to the bottom of the removable top plate III. The brackets I80 are each split as shown in Fig. 13 and provided with a clamping screw I8I to hold the stub shaft I19 in any adjusted position to which it may be adjusted by wrench-receiving sockets I 82. The rollers- I18 may be mounted upon the stub shafts I19 by means of ball bearings I83.

For the sake of compactness of operating parts and to maintain the overall length of the main frame at a minimum, I mount the feeding rope drum I84 within the top portion of the housing of the gear section 23, in a position where such rope drum will be concentric with the vertical axis of the tubular drive shaft 69. I also compactly locate planetary gear controlling mechanism within the hollowed out portion of the dishshaped bevel gear I12 and even within the hollowed out portion of the feed drum I84 itself.

The planetary gear control mechanism may be operated to effect rotation of the feed rope drum :89 either at a relatively slow feeding speed during kerf cutting operations, or at a relatively high handling speed when the mining machine is to be moved quickly from one place to another.

As shown in Figs. 3 and 4, an eccentric I85 is keyed to the hub I13 of the bevel gear I12. Surrounding the eccentric I85 is a bearing I88 on which is journaled a gear I81. The gear I81 is connected by welding, as shown in Fig. 3, to a horizontal plate I88 which has a bifurcated extension I89 provided with a slot I99 slidable with respect to a roller i9I carried by a vertical stubshaft I92 secured to .a stationary bracket I93 by a pin I94. The bracket I93 is secured by means of the machine screws I95 to the horizontal plate I 98, as shown in Fig. 4. Lubricant may be introduced by way of the conduit I96 to the bearing surfaces between the roller I9I and the stub shaft E92, as shown in Fig. 3.

Co-operating with the gear I81 is a second gear I91 which is mounted upon a hub I 98 by being welded thereto, as shown in Fig, 3. The hub I98 is spaced from the hub I13 of the dishshaped bevel gear I12, by journal bearing I99. To the bottom of the hub I98 is welded, as shown in Fig. 3, a sun gear 299 concentric. with the vertical axis of the tubular shaft 69. The sun gear 299 forms part of a planetary type of transmission as best seen by referring to Fig. 10.

Reverting to the power transmitting connections between the motor shaft 21 and the gear I91, it should be noted that rotation of the eccentric i855 will cause the gear I81 to walk around the gear I91 while meshing with the teeth thereof. The gear I81 will be held against rotation because of its being rigidly secured to the plate I88 by being welded thereto, as shown in Fig. 3. The plate I88 is held against rotation by the roller I9! on the stationary vertical shaft I92 which is rigidly secured to the plate I I8. But by reason of the slot I99 co-operating with the roller I 9!, the plate I88 will be free to oscillat as required by the eccentric I85.

The gear I81 has fewer teeth than the gear I91. In the accompanying drawings, the gear I81 has fifty-five teeth and the gear I91 has fifty-eight teeth. Consequently for each rotation of the dish-shaped bevel gear I12 there will be a complete rotation of the eccentric I85. If this is in a clockwise direction, the gear I91 will be rotated a slight amount correspondingly. For instance, for each rotation of the eccentric I85, gear I91 will move 1 of a rotation, or of a rtation. Consequently the speed reduction between the gear I12 and the gear I91 will be 58 to 3.

It will of course be obvious that this reduced speed will be transmitted from the gear I91 directly to the sun gear 299 through the hub I98. The sun gear 299, as shown in, Fig. 10, meshes with the four planetary gears 29I which are mounted upon four upstanding shafts 292 carried by a spider 208 mounted upon a cylindrical support 294 which is journaled upon the hub 295 of the feed drum I88, as shown in Fig. 3. The hub 295 is journaled on the bearing 29B carried by the cylindrical support 291, and the latter in turn welded to the bottom plate I 91, as shown in Fig. 3.

Each of the vertical shafts 292 is provided with an upper bearing portion 298 which extends, into a journal bearing for a roller 299.

An integralannular flange 2I9 is provided on the shaft 292 at its upper end portion in position to support the roller 299. The rollers 299 are adapted to roll upon the outer surface of the hub I98. A spring-pressed wiping member 2' is provided adjacent the upper end of said shaft 292 to provide lubrication for the roller 299. Below the annular flanges 2I9 the vertical shafts 292 each extends through the hub of the brake drum 2I2 which is formed integral with the spider 293. This can readily be seen by referring to Fig. which is a sectional plan view taken on the line 59, I9 of Fig. 3. A brake band 2I3 provided with a brake lining 2M is associated with the drum 2I2.

he planetary gears 295 are rotatably mounted with respect to the vertical shafts 292 by double antifriction roller bearings 2I5. Each of said planetary gears 29! is provided with a hub 2I6, to the upper portion of which the gear 29I is integrally attached, and to the bottom portion of which is attached a planetary gear 2I1. In other words, as shown in Fig. 3, the hub 2I6 carries both the planetary gear 29I and the planetary gear 2I1, and therefore both gears 29I and 2 I1 always rotate together.

Planetary gears 2I1 mesh with a ring gear 2I8 rigidly secured to the interior of the operating drum H39. It will thus be seen that the planetary gear 295 meshes with the sun gear 299, that the planetary gear 29I is connected to the planetary gear 2: I1, and the latter meshes with the gear 2I8 but is secured to the rope drum I84.

Not only do the planetary gears 29I mesh with the sun gear 299, but also with the ring gear 2I9 :hich is integral with the brake drum 229. The brake drum 229 is mounted upon a journal bearing 22I carried on the interior peripheral portion of the rope drum I89. Associated with the brake drum 229 is a brake band 223 provided with a lining 229.

By referring particularly to Fig. 10 of the drawings, it will be seen that the planetary gears 29I have fewer teeth than the planetary gears 2I1, the number of the teeth on each gear 29! being fourteen, and the number of teeth on each gear 2I1 being sixteen.

As will be described more fully hereinafter, the brake bands 2!? and 223 are so interlocked that it will be impossible to clamp both of them at the same time, and a single operating mechanism is provided whereby when one of said brake mechanisms is applied, the other is released, and vice versa. The brake bands may also be so adjusted that neither will be applied, under which condition power will not be transmitted to the rope drum I84 from the motor shaft 21 but will be free to be rotated by the operator grasping the feed rope and putting it out from the main frame of the machine and thereby freely rotating the rope drum.

By referring to Fig. 3 of the drawings, it will be seen that if the brake band 2| 3 is applied to the brake drum 252 to hold the same stationary, the rotation of the sun gear 299 will be transmitted to the planetary gears 2IJI and 2I1. When the brake drum 2l2 is held stationary, the axes of the vertical shafts 292 will also be held stationary because they are mounted on the brake 2I2 to revolve around the vertical axis of the tubular shaft 89 only when the brake drum 2I2 is free to rotate.

At the time that the brake H3 is applied to the drum 2I2, the brake 223 is released and therefore the brake drum 229 is free to rotate. Rotaheld stationary.

on the vertical bearings 292.

tion of the planetary gears 2M about the vertical stationary axes of the shafts 202, will be transmitted to the brake drum 220 but this will have no effect because the brake drum 220 at this time is free to rotate.

The rotation of the planetary gears 21'', however, will effect rotation of the annular gear 2l8 which is secured as by welding to the inner side of the large rope drum E34. It will thus be seen that when the brake 223 is released from the brake drum 223 but the brake 2&3 applied to the brake drum 2E2, rotation of the armature shaft 2'3 will rotate the sun gear 286, and the planetary gears 2!! will be rotated on vertical stationary axes 202 to effect rotation of the rope drum I84 on the vertical axis of the tubular drive shaft 69.

The planetary gears 2H, as shown in Fig. 10, are somewhat larger than the planetary ears 201, so as to secure a predetermined ratio of the number of teeth on the planetary gears 20! and 2H. In Fig. 10 this ratio is illustrated as being 14 to 16. It will thus be seen that when the sun gear effects a complete rotation of each of the planetary gears 26!, 14 teeth will be engaged, but 16 teeth of each of the planetary gears 2H will become effective in their meshing with the internal annular gear 2.!8 which is secured to the inner wall of the rope drum I84. The transmission of power to the rope drum from the sun gear 28!. will therefore be at a relatively fast speed when the brake 213 is applied to the brake drum 212 while the brake drum 22!! is released. This relatively fast speed of rotation of the drum 18 3 is useful in handing the mining machine when it is to be moved from one place in the mine to another while the cutting mechanism is not cutting a kerf.

When the brake 2 I3 is released and the brake 223 applied to the brake drum 220, a very slow feeding speed of rotation of the drum I84 will be secured. This feeding speed is used when the kerf cutter is cutting a kerf while the machine is being slid over the mine bottom by the feed rope Hi2 controlled by the retarding or guide rope 3 3.

When the brake 2 i3 is released and the brake 223 applied to the brake drum 220, the latter together with its inner annular gear 2l9 will be Since the rope drum M2 is free to rotate, the vertical shafts 202 are free to revolve about the vertical axis of the tubular drive shaft 69. Rotation of the sun gear 268 will cause rotation of the planetary gears 20! Since the brake drum 225i is held stationary together with its gear 2 i 9, the planetary gears 2M will walk around the stationary ring gear 219.

In making a complete rotation, the planetary gears 20%, each of which has 14 teeth, will have caused 16 teeth of each of the planetary gears 24? to mesh with the ring gear 218, because whenever any planetary gear 20! makes a complete rotation, the planetary gear Zllattached thereto will also make a complete rotation. In

other words, while the planetary gear 20! walks around the stationary gear 2! 9, the distance represented by 14 teeth, the planetary gear 2!! will attempt to walk around the gear 2l9, the distance represented by 16 teeth. The difference of two teeth represents the distance which the rope drum will be rotated during each rotation of the planetary gear 2H. That is to say, due to the difference in the number of teeth between the planetary gears 20! and 2H, it will be neceswill be released.

sary for the ring gear 2"! to rotate in response to the sun gear walking the planetary gear 20! around the ring gear 2I9whi1e the latter is being held stationary by the brake 223 being applied to the brake drum 22!].

The planetary gear mechanism shown in Fig. 3, controlled by the brakes applied to the brake drums 252 and 222, enables the power to be transmitted to the rope drum to rotate the same either at a fast handling speed or at a greatly reduced feeding speed. When both brake drums 2E2 and 220 are released by releasing the brakes 2E3 and 223, the rope drum 34 will be free to rotate so that the rope 32 on the rope drum I84 may be pulled out manually from the machine for the purpose of connecting it to an anchorage in the mine distant from the machine.

When power is transmitted to the rope drum 485 to rotate the same, a wide range of speeds of rotation of this rope drum may be obtained by partially applying either of the brakes 213 or 223 to the brake drums H2 and 22!}, so that slipping may occur between the brake drums and the brake linings 2M and 224. It should be understood, however, that when one brake is applied the other is released.

The mechanism for operating the brake bands 2E3 and 223 so that both may be released at the same time or either applied while the other is released, is shown particularly in Figs. 4, 6 and 7. The construction for applying one of the brake bands is substantially the reversal of the construction for applying the: other brake band. Upon the horizontal supporting plate H8 is secured, by means of machine screws H8, H8, a casting 32 6 having a pair of integral brackets 225 and 226. The left-hand bracket 226 as viewed in Fig. 6 is provided with an adjustable stop screw 22'! which co-operates with a springpressed lug 228 carried by one end of the brake band 2H3, the other end of which carries a lug 229 adapted to be received by spaced abutment means 232 carried by a slide plate 23!. The lug 228 is held against the stop screw 227 by a spring 232 co-operating with the stationary abutment 233 carried by the stationary casting 326. It can readily be seen by referring to Figs. 6 and 7, that if the slide plate 23l is moved to the left, the brake: band 253 will be applied to the brake drum 2l2, and if the slide 23E is moved to the right, as viewed in Fig. '7, the brake band 253 In other words, when the slide 23% is moved toward the left, the abutment means 232 will engage the lug 229 to apply the brake band 2 l3 to the brake drum 2E2, while the lug 228 is held by the spring 232 against the adjustable screw stop 22? carried by the stationary bracket 226 which is integral with the casting 326 and the latter secured rigidly to the horizontal supporting plate H8.

It should be noted that Fig. 6 is a section taken on the line 5-45 of Fig. 4, looking. in the direction of the arrows. Extending intothe lower portion of the bracket 225 is a horizontal adjustable stop screw 234 which corresponds in function to the stop screw 221 but is associated with the mechanism for applying the brake band 223, whereas the stop screw 22'! is associated with the mechanism for applying the brake band 2 53. As shown in dotted lines in Fig. 6, a lug 229' extends from one end of the brake band 223 into a recess between abutment means similar to that designated 23!! in Fig. 7. Also as shown in dotted lines in Fig. 6, a spring232 is associated with a lug 228' and the latter held by the spring 232' the stop screw 23 5.

By reason of the reverse arrangement of the mechanism for operating the brake band 223, the

slide plate 2 5i is moved to the left as viewed in Fig. '7 to apply the brake band M3 to the brake drum 2i2, but this slide is moved toward the right as viewed in Figs. 6 and '7 to eifect the application of the brake band 223 and at the same time release the brake band 213. It will thus be seen that whenever the slide 23I is moved in one direction to apply one brake band, the other will be released, and the interlocking is such that both brake bands can not be applied at the same time.

As shown in Fig. 6, a horizontal plate 3I8 secured to the walls I58, HE is provided to serve as a slide bearing for the slide plate 23I. By means of appropriate bracket plates 235, 235, as shown in Fig. '7, and by overhanging guide bracket integral with the casting 326, the slide plate 23E will be provided with suitable guiding devices to maintain the slide plate 23I in a rectilinear, oscillatory path of travel. Os-

cillatory movement may be imparted to the slide 23i to apply either the brake band 2I3 or the brake band 223, by means of a pitman 236 pivotally attached to the slide 23I by means of a keyed pin 23?. As shown in Fig. 4, the pitman 238 is pivoted eccentrically at 238 to a rotary cylinder 239 mounted in appropriate bushings in a cup Mil rigidly secured to an extension of the casting 326, as shown in Fig. 4. The upper end of the cup 2 35 may be provided with lubricating packing 2M. (Fig. 6.)

Secured to the cylinder 239 intermediate its ends is a worm gear 2 32 which meshes with a worm 2&3 (Fig. 4) carried by a shaft 2% extending through the adjacent vertical frame plate H6. The shaft 24 i is journaled in the roller bearings 2%, 2% carried by the removable tubular support 225. Keyed to the shaft 244 outside of the frame of the machine is an operating handle 2d? located adjacent to the horizontal wheel 666 and also adjacent the motor control box 29, as shown in Fig. 1.

As may be seen by referring to Fig. 1, a single operator standing on the leading side of the machine may have within his reach the wheel I555 for controlling the elevation of the kerf cutting unit, the reversing switch lever 3I for controlling the direction of rotation of the motor 26, the control lever 32 for effecting the starting and stopping of the electric motor 28, and the wheel 25? for controlling the speed of movement of the machine when slid over the mine floor by rotation of the drum I84 exerting a pull on the rope H32 while its free end is anchored to the machine and an intermediate portion of the rope Hi2 reeved through a pulley connected to an anchorage in the mine distant from the machine. When the hand wheel it? is moved to a neutral position. both of the brake bands 2l3 and 223 will be released and no power will be transmitted from the motor 26 to the rope drum I84, but the latter will be free to be rotated by the manual pulling out of the rope W2. Upon rotating the hand wheel 2-il in one direction, the rope drum will be rotated at a fast or handling speed when the machine is to be moved about the mine from place to place. During handling operations the rope i332 becomes a haulage rope and may be extended around the vertical rollers 38 and 39 and thence reeved through the pulley 33 so that when the free end of the rope W2 is connected to an anchorage in the mine and the rope drum I84 operated by the motor 26, the whole machine may be slid over the mine bottom rearwardly and longitudinally.

t should also be understood that the rope I 32 may be connected to the rope drum and mounted thereon in either direction, depending upon the direction of feeding movement of the mining machine. When the feed is opposite to that shown in Fig. 1, the butter bits 59 should be reversed and the guide rope 34 extended in an opposite direction to an anchorage in the mine.

Not only have I completely enclosed all of the operating parts shown in Fig. 3 within the housing of the main frame, except for the openings 248 and 249 for the rope Hi2, but I have also provided planetary gear mechanism to secure great reduction in speed and variation in speed of transmission to the rope drum I8 1 although employing a rope drum of relatively large diameter which has the advantage of prolonging the life of the feed rope m2 by reducing to a minimum the necessary bending thereof. The pull on the guide rope 34 is relatively small but the pull on the feed rope 32 during coal cutting operations is relatively very large and consequently it is desirable to use a very strong feed rope I92 and prolong its life by reducing to a minimum the necessary bending thereof.

The openings 268 and 249 shown in Fig. 2 may be provided on both sides of the machine, and likewise a guide pulley 25! may be provided on that side of the machine opposite to the guide pulley 259.

When the cutter bits 59 are arranged as shown in Fig. 1, and the feed and guide ropes I62 and 3 3 are arranged as shown in this view, the direction of feeding movement will be in accordance with the direction of the arrow 252, with the rope drum I84 operating in a clockwise direction as viewed in plan. While the brake 223 is applied and the brake 213 released, the sun gear 295 will transmit to the rope drum I84 a slow feeding speed.

During the feed of the kerf cutting mechanism in the direction of the arrow 252 of Fig. l, the retarding rope drum mechanism 35 will pay out the rope 34 as permitted by the slipping of the partially applied clutch or brake elements 47, 455 as controlled by the wheel To reduce the overall length of the main body of the machine when fed between an elongated conveyor and the coal face, the direction pulley 33 may be detached from the rear side of the motor section 22 by removal of the cotter pin 253 shown in Fig. 5.

When the feed rope I02 is extended from the machine and its intermediate portion reeved through a pulley on a snatch block connected to a roof jack at a point in the mine distant from the machine, it should be understood that the elevation of such snatch block may be adjusted vertically along the roof jack so as to cooperate with the anchorages of the free end of the rope to the machine, in securing the desired balanced pulls on the lower and upper portions of the mining machine structure considered as a whole.

When sumping operations are to be performed in the working face adjacent to the rib, the feed rope I82 is disconnected from its anchorage Mil shown in Fig. 1, and the rope I02 is reeved around the rollers 38, 39, pulley 33, roller 36, and pulley 25L and the free end of the rope IE2 connected toan anchorage between the cutter bar and the rib. The retarding rope 34 is then preferably extended from that side of the machine op-posite to that shown in Fig. l and so connected to suchanchorage in the mine near the rear end of the machine as to enable the controlling mechanism shown in Fig. 5 to cause such retardation of the rope drum 44 as to cooperate with the sumping of the kerf cutter into the coal face, first at an angle to the rib and then parallel thereto when the sumping cut is completed. After such sumping cut has been made, the connections of the ropes I02 and 34 maybe restored to the position shown in Fig. 1, whereuponthe feed of the kerf cutter may continue from the sumping cut in the direction of the arrow 252. A lateral extension 338 from the lower bracket 339 (Fig. 1) may be used to prevent the feed rope I02 from running off the roller 36.

It should be particularly noted that the dishshaped support I13 for the large bevelgear I12 not only'provides ample space for the planetary gear brake mechanism beneath and within the same, but also eliminates additional gearing meshing with the bevel pinion I69 while the shaft 2'1 is maintained in a relatively low position so that the bottom of the motor section 22 may make direct sliding contact with the mine bottom while rigidly connected to the gear section 23. as shown in Fig. 2.

Obviously those skilled in the art may make various'changes in the details and arrangement of parts without departing from the spirit and scope of the invention as defined by the claims hereto appended, and I therefore wish not to be restricted to the precise construction herein disclosed.

Having thus described and shown an embodiment of my invention, what I desire to secure by Letters Patent of the United States is:

1. In a mining machine, the combination with a supporting frame, of a chain cutter mounted thereon in position to cut a horizontal kerf in a mine vein, a vertical drive shaft connected to said chain cutter, a motor connected to said drive shaft, a rope drum mounted concentrically with said drive shaft, a gear train including planetary gear mechanism connected for transmitting power from said motor to said rope drum to rotate the latter and mounted concentrically with said vertical drive shaft, a rope mounted on said drum and adapted to have its free end connected to an anchorage in the mine, and means for controlling said planetary gear mechanism to vary the speed of rotation of said rope drum while said vertical drive shaft continues to rotate at the same speed.

2. In a mining machine, the combination with a frame, of a vertical drive shaft, a cutter mechanism, a motor, drive means for driving said cutter mechanism from said motor including said vertical shaft and a clutch, elevating means connected to be driven from said motor for adjusting the elevation of said cutter mechanism with respect to said frame including said vertical shaft and a clutch, a feed drum, and gear means for operating said feed drum from said motor including a clutch, all of said clutches being concentric with the axis of said vertical drive shaft to provide a compact mining machine.

3. In a mining machine, the combination with a frame, of a kerf-cutting unit including a cutter chain mounted for vertical adjustment with respect to said frame, a drum mounted on said frame, means for adjusting the elevation of said kerf-cutting unit, a motor, and means for selectively connecting said motor to said cutter chain, elevating means and drum comprising a clutch individual to each, the cutter chain clutch comprising a jaw clutch, the elevating means clutch comprising a friction clutch and the drum clutch comprising a planetary clutch, all of said clutches lyingin horizontal planes along a common vertical axis.

4. In a mining machine, the combination with a frame, of a kerf-cutter mounted for vertical adjustment on said frame, a drum mounted on said frame, elevating-mechanism for adjusting the elevation of said kerf-cu'ttenand power means for operating said kerf-cutter, drum and elevating mechanism comprising three individual clutches, one for each of said devices, all aligned onthe same axis and all mounted on said frame.

5. In a mining machine, the combination with a main frame, of a supplemental frame adjustable vertically relative to said main frame, kerfcutting mechanism mounted on said supplemental frame and operable in various positions of adjustment thereof, means for adjusting the elevation of said supplemental frame relative to said main frame, drive means for said kerf-cutting mechanism including a vertical shaft, a motor, drive means connected to drive said shaft from said motor, a clutch associated with the top of said shaft and operable to effect a drivin or non-driving relation between said shaft and said ke rf-cutting mechanism, a clutch associated with the bottom of'said shaft and operable to effect a driving or non-driving relation between said shaft and said elevating means, a cable drum journaled on the main frame on the axis of said vertical shaft and between said two clutches, and drive means for driving said drum from said motor including a controlling clutch positioned between said two first named clutches and on the axis of said vertical shaft.

6. In a mining machine, the combination with a main frame, of a kerf-cutting mechanism mounted on said frame, a motor, means for driving said kerf-cutting mechanism from said motor comprising a vertical shaft and a control clutch having an engaging element mounted for rotation with said shaft and on the axis thereof, means for feeding said mining machine while said kerf-cutting mechanism is operative to cut a kerf comprising a feed drum mounted to rotate on the axis of said upright shaft, and means for connecting said drum to said motor including a planetary clutch having a sun gear mounted concentric with the axis of said vertical shaft.

7. In a mining machine, the combination with a supporting frame, of a motor mounted on said frame, a horizontal kerf-cutter mounted on said frame, means including a vertical drive shaft for driving said kerf-cutter from said motor, clutch means concentric with said drive shaft for effecting a driving connection between it and said kerfcutter, a cable drum mounted on said frame concentric with said shaft and multiple speed planetary gear and clutch means concentric with said shaft for controlling connection between said shaft and said drum.

8. In a mining machine, the combination with a casing adapted to rest on and slide over a mine bottom, of a gear journaled to the under side of the top of said casing, a kerf-cutter mounted on top of said casing, mechanism connected to the hub of said gear within said casing and extending without the same for connection to said kerf-cutter to drive the same, elevating mechanism connected to said kerf-cutter, mechanism extending from the hub of said gear downwardly and along the bottom of said casing to drive said elevating mechanism, a feeding rope drum dishshaped on its upper side and journaled'within the lowerportion of said casing concentric with said gear, power-transmission mechanism between said gear and the dish-shaped upper side of said rope drum, a motor connected to said gear to drive the same, and means for controlling said power-transmission mechanism to regulate the speed of rotation of said rope drum.

9. In a mining machine, the combination with a supporting frame, of 'a motor on the rear end of said frame, a kerf-cutting unit mounted in top cutting position on said frame to cut a horizontal kerf spaced above the mine bottom, rope drum feeding mechanism comprising a rope drum mounted in said frame 'to rotate on a vertical axis in advance of said motor with a rope leading'from the forward side of said drum laterally from said frame near the front end thereof to and from an anchorage in the mine extraneous to the machine, an anchorage on the kerf-cutting unit for the free end of said rope, power-transmission mechanism between said motor and said kerf-cutting unit and comprising a vertical extensible shaft concentric with said rope drum, means connected between said power-transmission'mechanism and said ropedrum to drive the latter, and'elevating mechanism operatively connected to said'shaft and located in advance of said rope drum adjacent the front end of said frame. 7

10. In a mining machine, the combination with a supporting frame adapted to rest on and slide over a mine bottom, of a kerf-cutting unit mounted on said frame for'adjustment relative thereto,

power-transmission mechanism comprising a vertical shaft connected to said kerf-cutting unit to drive the same, rope drum feeding mechanism comprising a rope drum concentric with said shaft and having a rope connected thereto and leading laterally of the forward end portion of said frame, power-transmission mechanism connected to said rope drum, elevating mechanism between the front end portion of said frame and said kerf-cutting unit, and operating connections extending along the bottom portion of said frame from the lower end of said shaft to the lower end of said elevating mechanism.

11. In a mining machine, the combination with a pan adapted to rest on and slide over a mine bottom, of a casing secured to and mounted on said pan, a kerf-cutting unit mounted on top of said casing for adjustment in elevation relative thereto, power-transmission mechanism within said casing comprising a vertical shaft extending out from the top of said casing to said kerfcutting unit to drive the same, feeding mecha nism for the mining machine comprising a rope drum concentric with said vertical shaft and having a rope wound thereon and leading from the front side thereof through one side of said casing near the front end thereof for connection to an anchorage, elevating mechanism between the front end portion of said casing and said 'kerfcutting unit, and power-transmission mechanism extending along said pan between the lower end of said shaft and the lower end of said elevating mechanism.

LEWIS E. MITCHELL. 

